Roadable wide working-width machine



y 23, 1954 M. RONNING 3,142,144

ROADABLE WIDE WORKING-WIDTH MACHINE Filed July 3. 1961 7 Sheets-Sheet 4 FIG! 5' 58 5' [I we uvmvroa MJRf/A/ POAbV/Milrroavaxg July 28, 1964 NG ROADABLE WIDE WORKING WIDTH MACHINE Filed July 5, 1961 7 Sheets-Sheet 6 -JEA INVENTOR. MART/1v Row/W414- Jrronmar:

United States Patent 3,142,144 RQADABLE WIDE WORKING-WIDTH MACHINE Martin Ronning, Minneapolis, Minn., assignor to Archer- Daniels-Midland Company, Minneapolis, Minn., a corporation of Delaware Filed July 3, 1961, Ser. No. 121,768 18 Claims. (Cl. 56-228) This invention relates to machinery of the type which has a transverse over-all dimension, or working-widt that is larger than the longitudinal dimension, as measured parallel to the normal direction of movement of the machine under working conditions. Exemplary machines of this type include agricultural machinery such as flail-chopper harvesting machinery, road working machinery such as sweeping and windrow-working machinery, and the like. For efficient operation, the working width of machines of this character together with the necessary clearance width of the tractor vehicle by which they are moved, substantially exceed the width which may permissibly be moved over usual public highways. Accordingly, the movement of such machines has been restricted.

It is an object of the present invention to provide a wide working-width machine which is capable of being managed so that it may be towed from one operation to another in a direction at right angles to its normal working direction wherein the machine has a narrower width and may be towed over public highways. It is another object of the invention to provide a wide working-width machine having provision for moving it in the working direction during its normal operation, and for moving it on self-contained wheels in a direction at right angles to the working direction when towing the machine from place to place. It is a further object of the invention to provide a machine of the aforesaid character that may have the wheels adjustably positioned thereon without jacking, etc. It is another object of the inven tion to provide a machine of the aforesaid character capable of being operated by one man, without additional help. It is a further object of the invention to provide an improved flail-chopper agricultural machine of exceedingly rugged construction and of wide cutting width. It is another object of the invention to provide a flail chopper agricultural machine of wide workingwidth capable of being manipulated by one man during normal working, and capable of being manipulated by one man for conditioning the vehicle for a towing operation at right angles to the normal working direction for moving the machine from place to place.

Other and further objects are those inherent in the invention herein illustrated, described and claimed, and will be apparent as the description proceeds.

To the accomplishment of the foregoing and related ends this invention then comprises the features hereinafter fully described and particularly pointed out in the claims, the following description setting forth in detail certain illustrative embodiments of the invention, these being indicative, however, of but a few of the various ways in which the principles of the invention may be employed.

The invention is illustrated with reference to the drawings wherein FIGURE 1 is a plan view of the exemplary machine embodying the invention, parts of the machine being broken away to more clearly illustrate other parts of the machine;

FIGURES 2 and 3 are right end elevational views taken in the direction of arrows 2 and 32 and 3 of FIGURE 1, FIGURE 2 illustrating the machine with the working head of the machine in normal operating condition and FIGURE 3 illustrating the machine with the working head in an elevated condition. FIGURE 3 also diagrammatically illustrates in dotted lines the general arrangement of the belt and pulley arrangement that is on the left side of the machine.

FIGURES 4 and 5 are sectional views through the machine taken along the line and in the direction of arrows 4 and 54 and 5 of FIGURE 1, and wherein FIGURE 4 illustrates the machine in normal working condition and FIGURE 5 illustrates the machine with the cutting head thereof raised to an elevated position. FIGURE 6 is an enlarged fragmentary sectional view taken along the line and in the direction of arrows 66 of FIGURE 4.

FIGURE 7 is a fragmentary end elevational view from the right end of the machine showing the cutting head of the machine elevated and a bogey wheel attached thereto for transport conditions.

FIGURE 8 is a fragmentary elevational view, partly broken away, and taken along the line and in the direction of the arrows 8-8 of FIGURE 7.

FIGURE 9 is a fragmentary sectional view taken along the line and in the direction of the arrows 99 of FIGURE 8.

FIGURE 10 is an enlarged fragmentary vertical, left end elevational view taken along the line and in the direction of arrows 1010 of FIGURE 1.

FIGURE 11 is a fragmentary vertical sectional view taken along the line and in the direction of the arrows 1111 of FIGURE 1.

FIGURE 12 is a right hand end elevational view, corresponding to FIGURE 2, except with the cutting head of the machine in elevated condition with a bogey wheel in place, according to FIGURE 7, and illustrating, in the background, the wheels of the tractor vehicle of which the machine is moved. ,The right hand wheel is sown in a raised transport condition in dotted lines.

FIGURE 13 is an enlarged fragmentary plan view of the right hand end of the machine as shown in FIGURE 1, and illustrating the right main wheel of the machine in field or normal working conditions.

FIGURE 13A corresponds to FIGURE 13, but shows the right main wheel of the machine moved to transport position.

FIGURE 14 is a rear elevational view of the machine together with a portion of the rear wheels of the towing vehicle, showing the machine actuated to transport condition. 7

FIGURE 15 is an enlarged fragmentary vertical sectional view generally taken along the line and in the direction of arrows 1515 of FIGURE 14 other than the right hand wheel has not been turned to a touring position as illustrated in FIGURE 14.

FIGURE 16 is an enlarged fragmentary vertical sectional view taken along the line and in the direction of arrows 1616 of FIGURE 14.

FIGURE 17 is an enlarged fragmentary sectional view corresponding to FIGURE 11 other than that it illustrates the second embodiment of mechanism for forcing the tow bar to an inclined transport position while said tow bar is connected to a tractor.

Throughout the drawings, corresponding numerals refer to the same parts.

In the description herein the invention is illustrated with reference to an agricultural machine of the fiailchopper harvester type, but it will be understood that the particular type of machine to which the invention is applied may be varied.

Referring to the drawings, particularly FIGURES 1 and 14, the invention comprises a main frame generally designated 10 which, as here illustrated, is composed of a framework made of tubular steel and plates welded together. The frame 10 includes a right end portion 11 which connects with an angularly disposed .form a mounting for the hydraulic cylinder 34.

portion 12 which in turn connects with a rearwardly displaced portion 13 that is parallel to the portion 11. These portions of the frame are tubular, in this illustration. The portion 13 of the frame extends into a box framework 14 composed of upper and lower plates, which extend to the left end 15, and also extend forwardly and outwardly at 16. These portions of the frame 14-15-16 comprise upper and lower plates that have vertically stiffening walls at 16, 17 and 18 and elsewhere as required to provide mechanical rigidity. At 2t) there is provided a pivot on which the tow bar 21 is adapted to swing from the position shown in full lines in FIGURE 1 to the position shown in dotted lines in the same figure.

Referring to FIGURES and 11, it will be observed that the upper plate 22 is spaced from the lower plate 23 by an amount sufiicient to accept the tow bar 21 which is preferably tubular. At the rear end of the tow bar there is provided a horizontal pivot 24 which connects into a knuckle 25 through which the vertical pivot 20 extends. As a consequence, the tow bar is, except for the confining effect of plates 22 and 23, free to move up and down, as shown by the double arrow In the normal working position represented by FIGURE 1 (full line) and FIGURE 10, the tow bar 21 is neatly confined between the plates 22 and 23, and in effect provides a solid projection to the outer end 26 of the tow bar where an eye is provided for receiving the pin 27 through the hitch 28 of the towing vehicle V. However, as shown in FIGURE 10, the lower plate 23 is provided with a downwardly extending trough space 28 as defined by the walls 29, 30 and 31. This space is a trough which slants downwardly from the position of pivot 20 to the outer edges of the plate 23, and the trough access is aligned with the axis of the tow bar 21, when it is in the towing position as shown in dotted lines of FIGURE 1. Therefore, when the tow bar 21 is in the dotted line position of FIGURE 1, the outer end of the tow bar may swing down in the direction of arrow 25D and motion of the tow bar in this direction is provided by a hydraulic jack device, the details of which are shown in FIGURES 1, 10 and 11. Thus, in FIGURE 1 there is provided a pivot bar 32 which extends over the side of the plate 22 so as to The plunger 35 of the cylinder is adapted to push against the tow bar 21 and force the tow bar down into the trough space 28 until the tow bar is in abutment with the bottom plate 30 of that space. In so doing the tow bar pivots around the pivot 24-, see FIGURE 10. The walls 29 and 31 of the space 28 serve to confine the tow bar 21 when it is pushed into the space 28, and hence the tow bar is held fixedly in the position shown in dotted lines in FIGURE 1.

When the tow bar is in the full line position shown in FIGURE 1 a pin 37 is placed through a suitable aperture in the plates 22 and 23, so as to prevent the tow bar from swinging. At the end of the main frame 10 there is provided a fixed axle 40 on which is mounted a rubber tire wheel .1, Wheel 41 being the left main wheel of the machine.

At the right end of the tubular frame 10 there is provided the Wheel 42 which is the right main wheel. This wheel is mounted, as shown in detail in FIGURE 13. Thus on the tubular frame portion 11 there are welded two generally vertical plates 44 and 50 which form a corner and serve as a mounting for the hinge pin 46. The plate 44 is parallel to the working direction, i.e. the longitudinal direction of the machine as shown by the working direction arrow W of FIGURE 1. The plate 50 is at right angles to the plate 44 and is parallel to the towing direction, as shown by the arrow T of FIGURE 1. The wheel 42 is provided with an axle 47 which is Welded onto a swing plate 48 which has upper and lower clip plates of which the plate 49 is' parallel inner edges 66a and 68a.

shown. These are apertured to receive the vertical pin 46. The plate 48 extends rearwardly and at the forward end thereof, there is welded in a cap screw 51 that is positioned to be able to pass through a notch suitably disposed in the forward end of the plate 44. At the rear end of the plate 48 there is extended a similarly disposed stud 52 which is so positioned as to pass through a suitably disclosed notch in the plate 50. In the working position as shown in FIGURE 13 plate 43 rests flatly against the plate 44 with the stud 51 extending through the notch in the plate 44 where it is held by a nut 53. In the towing position the nut 53 is removed and the plate 48 is swung on the axis of pin 46 until it reaches the position where the plate 44 is solidly against the plate 50 with the stud 52 extending through the notch of the latter plate. There plate 45 is secured by the nut 53 which is threaded on the rear stud 52, it being mentioned the plate 56 has offsets 45 welded to frame 11 so that sufficient space for threading the nut on the stud is provided between the main body of the plate 50 and the frame 11. Thus, the Wheel 42 may be set so as to run in the working direction W or in the towing direction T, and in either position is held solidly.

On the frame 10 there are disposed two vertically arranged space pairs of tracks 64} and 61, see FIGURES 14, 15 and 16. Referring to FIGURE 15 on the frame member 1 1 there are welded the two vertically disposed track pieces 62 and 63 which are positioned so that their inner edges 62a and 63a are in spaced parallel relation. At one place across the track pieces there extends a tie plate 64 having the notch 64a in it, which is so disposed so as to receive the floating frame generally designated 70, to which reference will hereinafter be made. The tie plate 64 is accordingly a bottom stop for the floating frame. Across the top of the track pieces 62-63 there is bolted another plate 65, plate 65 also serving as an anchorage for certain spring balancing mechanism.

The track 61 is similar to track 60 and in this instance is welded to the upper plate 22 of the frame portion 14, which is on the left side of the main frame. The track 61 is composed of two pieces 66 and 68 having spaced These tracks are permanently tied together by the cross tie 67 which has a rounded notch 67a which serves as a bottom stop for the floating framegenerally designated 70 as will be described. Here again the upper ends of the track members 66 and 63 are tied together by a plate 69 which is bolted in place. A stay brace 71 is provided for the track 61 as shown in FIGURE 14.

The floating frame generally designated 70 is illustrated in FIGURES 1 and 14. It is composed of tubular pieces welded together, these piecesbeing parts 72, 73, 74, 74A and 76. The particular shape of the main frame 10 and the floating frame 70 is necessitated by the position in the illustrated agricultural machine of a blower generally designated 75. Both frames 10 and 70 are made so as to provide space for the blower, and non-interference between the various frame members and the blower casings.

The floating frame is mounted on the main frame by means of wheels which travel in the tracks 60 and 61, the wheel mechanisms being similar. Thus in FIGURE 15 of the floating frame 7 0 has upwardly extending spaced pairs of plates 76 and similar downwardly extending spaced pairs of plates 77 which provide mountings for the pivots 78 and 7 respectively. Pivot 79 serves as a pivot for the wheel 8t) and pivot 78 serves as a pivot forthe wheel 81. These wheels roll up and down within the confines of the inner surfaces 620 and 63a of the verticaltrack 60 with the frame 70 normally resting in the notch 64a of plate 64. Extreme upward motion of this end of frame 70 is prevented by a contact of the frame with the under edge 65a of the upper tie plate 61 on the tracks. Similarly, as shown in FIGURE 16, the frame at its left end is provided with downwardly extending spaced plates 82 which mount pivot 83 on which the wheel 84 revolves, upwardly extending space plates 85 providing a pivot 86 with the wheel 87. Here again the wheels move up and down within the confines of the space defined by surfaces 66a and 68a of the track 61, the left end of the frame 70 normally resting in the notch 67a of the plate 67, upward limit of movement being the under surface 69a of the plate 69.

At the left end of the frame 70, see FIGURE 14, there are downwardly extending frame pieces 90 terminating at plate 91 to which a gear box 92 is suspended. This gear box has a forwardly extending input drive shaft 94, see FIGURE 1, which is connected through a universal joint 95 to a spindled extensible drive shaft 96 which is supported on an outboard bearing 97 of the selfaligning type. The outer end 98 of the drive shaft, not illustrated, is connected to a conventional power takeoff that is provided with another universal joint, not illustrated. The last mentioned universal joint is in turn connected to the power take-off of the towing vehicle V. Accordingly, as the drive shaft 96 rotates, the motion will be transmitted through the gear box 92 to its output shaft 99, see FIGURES 1 and 14. The output shaft 99 is carried by suitable bearings 100 and 101 mounted by appropriate depending braces 101A secured to frame 70 for movement therewith, and has a drive pulley 102. The drive belt 108 extends around pulley 102 and under a pulley 104 on the recutter drive shaft 105, next over the idler pulley 103, and thence around the pulley 106A on shaft 106 (see FIGURE 3). While the details of the particular harvester mechanism illustrated in this application may be varied according to the harvesting machine, it may be stated that this harvesting machine has a main drive shaft 99, on which the fan of blower generally designated 75 is mounted. The blower housing 75A is permanently afiixed with reference to the floating frame '70 and has an inlet that opensto the outlet 110A of the recutter housing. On this same shaft 99 is the pulley 102 previously described over which runs the belt 108 which drives the pulley 104 on the recutter drive shaft 105 to drive the recutter mechanism 110. Belt 108 also drives the pulley 106A and shaft 106 of the flail chopper mechanism generally designated 111.

The recutter drive shaft 105 extends all the way through the machine to the left end 112 whether it is connected by a suitable belt 113 to a pulley 114 on the shaft 115 that drives the screw auger 116. The auger has two sections 117 and 118 which deliver according to the direction of arrows 119 and 120 to the inlet of the recutter 110, and from the latter the recut forage is delivered to the inlet of the blower 75 from which it is discharged via the pipe 122 to a spout (not shown) delivering to a towed wagon box behind the recutter machine.

The axis of the shaft 99 is thus fixed with reference to the floating frame 70 and upon this frame 70 there is mounted the entire harvesting mechanism, which has a floating action, relative to the main frame 10. Thus, referring to FIGURE 12, the shaft 99 which is output shaft of the gear box 92, and also the shaft of the blower 75, has on it a suitable bearing to which there is attached a forwardly extending radius arm 125 (see FIGURE 1 and FIGURE 14). The right end of the floating frame 70 terminates just to the right of the vertical track 60 and it is provided with a pivot 126, on which a similar radius arm 127 likewise extends forwardly. It is noted that the axis of the pivot 126 coincides with the axis of the power shaft 99 at the other end of the frame. Accordingly the two radius rods 125 and 127 move about the same pivoting axis, on frame 70. Both of the radius rods 125 and 127 extend forwardly to the heavy transverse tubular frame member 130 of the cutter head, which is composed of sheet metal suitably shaped to receive and support the cutting mechanism. Thus, the cutter frame includes curbed housing pieces 131, 132 hinged together at the hinge line 133, an auger conveyor portion 134, end plates 135 and 136, two or more ground shoes generally designated 137 intermediate the end plates, and shoes 138 on either end plate (see FIGURES 2 and 4). All parts are welded into a complete and stable whole, and the cutter housing can thus move arcuately up and down as shown by the double arrows 14014 and 140d (see FIGURE 5).

' Extending downwardly from the tube 130 are several auxiliary ground shoes 137 having a forwardly curved plate portion 137A which is parallel to the path of movement of the cutter blades. These plates are suitably supported by internal bracing and have a ground shoe plate 1373. The side plates of the cutter housing are tied together at the front by a bar 141. Shoes 138 are flanged horizontally outwardly of the end plate and have vertically extending flanges secured to the end plates. The upper front ends of shoes 138 are located adjacent bar 141. The auxiliary shoes 137 are set a little higher than shoes 138 and act as a safeguard to raise the cutting elements over uneven ground and to a large extent prevent the cutting elements contacting the ground.

On the side plates are mounted suitable journals 142 and 143 which serve to rotatably support the axle 144 of the flail cutter. The flail cutters are carried by a tubular shaft 146, having a plurality of rings 147 spaced axially thereon. These rings are apertured to receive through pins 148 upon which the flail cutter 149 is pivotally mounted. A suitable spring clip not shown is provided on the pins 148 to prevent them from moving endwise, and for removal there is provided an aperture in one of the end plates 135 or 136 through which the pins 148 may be withdrawn for replacing the flail cutter. As illustrated, the flail cutters have shank 149C and a bolting plate 149A, on which the cutter head 149B is attached by suitable bolts. The flails are free to swing on the pins 148 from the position shown in FIGURE 5, which is a position at rest, to a working position as shown in FIGURE 4. The rotation of the shaft 144 is in the direction of arrow 150A and the cut material is thrown by the flail upwardly and reaiwardly in the direction of the arrows 151 where it lodges in the space occupied by the screw auger generally designated 116. The auger rotates in the direction of arrow 152, and moves the cut material to the inlet 154 of the rechopper 110, as previously described. Several spaced shoes 137 are provided along the width of the cutter housing, as shown in dotted lines at 137E, 137F and 137G in FIGURE 1. The shoe 137G is preferably made broad so as to allow adequate ground contact on the flat crest of water control ridges in irrigated fields. The wall 137AW of shoe 137G, FIG- URI-IS 1 and 7, serves as a flat surface for mounting the bogey wheel assembly generally designated 150, to which reference will later be made.

The weight of the cutter housing is carried as follows. On the main frame 10 there is a forwardly extending perch 155 which provides three walls 155A, 155B and 155C (see FIGURES '1, 4 and 5). Through these walls there passes a pivot 156 for pivotally mounting the single tree 157, the lower end of the single tree 157 having the parallel bar spring mechanism 163, 165 attached. On the single tree 157 there are two parallel bars 158 and 159 on which slide the sleeves 158A and 159A. Springs 158B and 159B respectively surround a bar-sleeve, the upper ends of the springs being retained in place by pins 160 secured to the exterior of the sleeves. The upper ends of the sleeves are solidly connected to an upper single tree 161, which is attached at pivot 162 to a frame piece 164 (see FIGURE 1) on the rear part of the auger housing 131. Therefore, the two springs 15812 and 1591) provide an upward thrust from the main vehicle frame 10 to the approximate mid-position of the cutter housing.

Adjacent the right radius rod 127 there are upwardly extending frame members 166 fastened to the rear of the i auger housing, and these are aligned with the right track 6%, so that a pair of springs 167 can be attached between the upper end of the frame 166 on the auger housing and to an anchorage 168 which is adjustably secured to the upper end of the track frame plate 65. The springs 167 thus produce a rotational force in a direction opposite to the weight of the cutter housing while the springs 15812 and 1591; produce an upward thrust.

In order to provide for mechanical lifting of the cutter housing, to swing it about the axis of pivoting on pivot 126 and shaft 99, as previously described, there is also provided a hydraulic jack mechanism. The same pin 156 which serves to anchor the lower single tree plate 157, see FIGURE 4, also serves as an anchorage for one end of the hydraulic jack assembly which is composed of a link of two members at 184) and a hydraulic cylinder at 181, see FIGURES 4 and 5. The link 180 is simply a bar channel of steel set mounted to pivot on pin 156 and positioned so as to bottom against the plate 155D secured to the bottom plate 155E of perch 155 when in the position shown in FIGURES 4 and 5. At the outer end of this link there is another pivot 182 which is at the bottom end of the cylinder 181, the piston-piston rod 183 of which is pivoted at 184 to a suitable bracket 1&5 on the rear part of the auger housing 134 of the cutting mechanism. The hydraulic cylinder 181 is a two-way hydraulic cylinder, and therefore may be jacked up or down, thereby effectively changing the dimensions between the pivots 182 and 184. As this dimension is increased, by extending the hydraulic piston 183, force will be applied sufficient to swing the cutter housing from the position shown in FIGURE 4 to the position shown in FIGURE 5, in which case the cutter housing is well off the ground. In this condition the links 13% rest solidly against the step 155D, which is a part of the frame 155 extending from the main vehicle frame 19. However, when the length of the hydraulic link is decreased, the cutter mechanism will be lowered gradually to the position shown in FIGURE 4, and in this condition the cutter mechanism is approximately balanced, so that very little weight of the cutter housing and mechanism is carried by the shoes 138 which slide along the ground. In the event shoes 137 or 138 should engage in obstruction, it will cause the cutter mechanism housing to be elevated (and also the floating frame to be elevated if the obstruction is sulficient) and this merely swings the link 180 around the pivot 156 (without causing movement of the piston in the cylinder) until the obstruction is cleared. Then the cutter housing resumes the position shown in FIGURE 4. The floating frame '70 normally rests in the notches 64a and 67a of the track frame 62 and 61 respectively, see FIGURES l5 and 16, but if the right or left hand portions of the cutter housing should be elevated by their shoes engaging a ground obstruction, or due to tilting of the terrain, the frame 70 will rise off of both or one or the other of the notches 64A or 67A. It is to be noted that the tracks are suliiciently wide to permit a little tilting movement of the floating frame wheels and thereby permitting the floating frame lifting out of only one notch. Also the tracks may desirably be provided with flanges (not shown) to limit the transverse rnovementof frame 70 relative to frame lit] but at the same time permit the tilting movement in a vertical plane. Thus, the frame 70 is capable of floating and of lifting one end or the other, and the cutter housing is in turn capable of arcuate up and down movement with reference to the frame 7t It will be appreciated that the forces transferred through the springs 15813 and 159B to the cutter housing will in part be utilized in relieving the weight on the rear ends of the radius rods 125 and 127. In other words, the more force that is transferred directly from the cutter housing to the main frame via springs 158B and 15913, the less force is carried elsewhere through the framing 70 to the tracks 6% and 61.

Referring to FIGURES 1, l4, 7, 8 and 9, the bogey wheel assembly consists of a transport wheel 190 which is journalled on an axle 191. At the outer end of this axle there is an upwardly extending frame plate 192 that is braced by the gusset 193. Inside of this frame plate there are provided an inwardly extending plate 194, provided with notches 195 shaped so as to receive the bar 141 of the cutter frame. When received in the notch 195, the plates 192-194 may be attached to the bar 141 by a clip 196 that is held in place by the bolt 197. This prevents the plate from sliding around on rod 141.

At the inner end of the shaft 191 there is a flat plate 198 provided with a suitable notch 199 for receiving a pin 2% therein. This pin is welded to one of the flat sides 13'7AW of one of the ground engaging shoes of the cutter frame, the position of this flat side plate 137AW being such that when the bogey wheel is in place its axle 191 will be approximately aligned with the center of the tread of wheel 42, which is the right wheel of the main frame.

It is a special feature of this invention that the relatively heavy machinery may be manipulated by a single operator for moving all of the mechanisms from the field working condition to the road transport condition. This is accomplished as follows: The hydraulic cylinder 181, see FIGURE 4, is actuated (in thedirection of arrow 181A) was to move the cutter head (working assembly) to its most elevated position with the floating frame re maining in its lowermost position (see FIGURE 5 Now, a lock pin 205 is extended through appropriate apertures formed in plates A, 15513 and link to prevent said link pivoting about pivot 156 (see FIGURE 6). Next the bogey wheel assembly is attached as shown in FIG- URE 7 and then the cutter head is lowered so as to put the weight on the bogey wheel. This is done by retracting piston rod 183 (arrow 181B) while the tractor V is in its usual field working position with the tongue 21 as shown in full lines in FIGURE 1. With the cutter housing pushed down, there is a tipping action developed about an axis through wheels 141, 151 with the weight being placed on the bogey wheel assembly 15% and the left main wheel 41, which accordingly slightly elevates the right main wheel 42, such as illustrated in FIGURE 12 other than the tractor and tow bar have not been positioned as illustrated in this figure. At this time the left hand end of the floating frame is lifted off the bottom stop while the right hand end remains in the bottom stop. when this occurs the right main wheel may readily be swung to the transport position, corresponding to FIG- URE 13A and 14, and locked in place by tightening the nut 53 on the stud 52. The hydraulic cylinder 181 which controls the cutter housing is then operated in a direction to raise the housing (arrow 181A) and this lowers the right main wheel 42 until all three wheels are on the ground. The securing pin 37 of tongue 21 is then removed, and the tractor V is maneuvered so as to swing the tongue 21 from the full line to the dotted line position as shown in FIGURE 1. The hydraulic jack 34 is then operated so as to swing the tongue 21 down into the space 28, see FIGURES 10 and 11, and the efiect of this is to elevate the left main wheel 41, to the transport position shown in FIGURE 14, and the vehicle is then immediately ready to move over the highways to another location. A pin (not shown) may be provided for holding the tow bar in the transport position.

A second embodiment of apparatus for forcing the tow bar to an inclined transport position when the tow bar is connected to the tractor V is illustrated in FIGURE 17 and generally designated 216). The mechanism 210 includes a pair of parallel mounting plates 211 Welded to the upper plate 22. A pair of spaced pivot arms 213 are pivotally mounted between plates at their midportions by pivot 213, the arms being retained in spaced relation by spacers 214 on pivot 212. The piston rod 215 is pivotally secured between the one ends of the pivot arms by pivot 216, piston rod being movable between a retracted position as illustrated in FIGURE 17 and an upper position by the piston cylinder combination 217. The piston cylinder combination in turn is mounted on a plate 219 which is welded to the plate 18.

Between the opposite ends of the pivot arms is a pusher rod 220 which at its upper end is pivotally secured by pivot 221 to the arms 213. The lower end of the pusher arm is positioned to engage the tow bar, similarly as the rod 35, to force it into an inclined position and thereby elevate wheel 41 when the tow bar is connected to the tractor V. A plate 223 limits the pivotal movement of the pusher rod to prevent it from pivoting out of a position to force the tow bar to an inclined position.

By applying hydraulic pressure to the cylinder 218 the piston rod 215 is forced in an upward direction to in turn cause the pivot arm 213 to move the pusher rod 220 in a downward direction. Once the pivot arms are moved to a position to force the tow bar to a transport position as indicated in dotted lines, a lock pin (not shown) may be inserted in the apertures 227 and extended to the then aligned apertures 223 formed in the pivot arms and thereby positively retain the tow bar in an inclined position. It is to be understood that a manually operated jack may be mounted on the plate 219 in place of the cylinder and piston rod 217, 215 for moving the pivot arms in the aforementioned manner. However, it is preferred that hydraulic means such as described heretofore be used. It is to be mentioned that the blower, recutter, auger, fluid chopper mechanism and associated members attached to the radial arms and floating frame are also referred to as a working assembly. Thus it may be seen that other types of wide working width heavy machines that have working assemblies movable between a raised position and a lowered position may be advantageously provided with a bogey wheel assembly and tow bar mounting and forcing means as described heretofore.

As many apparently widely different embodiments of this invention may be made without departing from the spirit and scope thereof, it is to be understood that I do not limit myself to the specific embodiments disclosed herein.

What I claim is:

1. For being pulled by a power vehicle, an agricultural implement having a working width of a substantially greater dimension than its overall length comprising a main frame, a first and a second wheel, means for mounting said first wheel on one transverse side of said main frame to roll in a working direction, means for selec-.

tively retaining the second wheel on the opposite side of the main frame for rolling movement in a transverse di rection and a longitudinal working direction, a tow bar, means connecting one endsof the tow bar to the frame adjacent the side on which the first wheel is mounted to alternately extend generally in a working direction and at right angles to the working direction, the last mentioned means including means for forcing the tow bar to move its opposite end in a downward direction relative to the frame to exert a tipping force on the frame when the tow bar is connected to a towing vehicle and retain the tow bar opposite end in a relative downward position, a bogey wheel, and means for removably connecting the bogey wheel to the main frame in longitudinally spaced relation to the second wheel to roll in a transport direction.

2. The apparatus of claim 1 further characterized in that the means for connecting the bogey wheel to the main frame includes a working assembly for performing a working operation adjacent the ground, means mounted on the main frame for selectively raising the working assembly to an elevated position and lowering it to a working position adjacent the ground and cooperating means on the work assembly and connected to the bogey wheel for removably securing the bogey wheel to the work assembly on the same side of the longitudinal axis of the main frame as the second wheel.

3. The apparatus of claim 1 further characterized in that the tow bar forcing means includes a piston cylinder combination having a push rod to exert a force against the tow bar, said combination mounted on the frame to overlay the tow bar in a transport position.

4. The apparatus of claim 1 further characterized in that the tow bar forcing means includes an elongated pivot arm, means mounting the pivot arm on the main frame to pivot about its midportion and have one end thereof overhang the tow bar in the transport position, a vertical push rod mounted on the one end of said arm to engage the tow bar and means mounted on the frame for forcing the opposite end of the pivot arm to pivot about the arm pivot axis.

5. In a heavy machine, a main frame, at least two wheels, means for mounting a wheel on each transverse side of the main frame, a pair of transversely spaced, vertically extending tracks mounted on said main frame, a transversely extending floating frame, said floating frame including a transverse frame member, means connected to said frame member for mounting it for floating vertical movement on said tracks, stop means for limiting the vertical movement of the transverse frame member in both an upward direction and a downward direction relative said tracks, a pair of transversely spaced radial arms connected to the floating frame for movement therewith and arcuate movement about a common transverse axis, said arms extending in a longitudinal direction outwardly beyond the main frame, a working assembly secured to the outer ends of said arms for movement therewith for performing a working operation adjacent the ground, and means mounted on the main frame and connected to the Working assembly for arcuately moving it about the radial arm pivot axis between a raised transport position and a working position adjacent the ground.

6. The apparatus of claim 5 further characterized in that the last mentioned means includes a pistoncylindef combination, a linkage pivotally connected at one end to the main frame and at the other to one end of said piston cylinder combination, means for limiting the pivotal movement in a direction to lower said working assembly, and extensible means connected to the main frame for supporting part of the weight of the working assembly and transferring it directly to the main frame.

7. The apparatus of claim 6 further characterized in that the working assembly has ground engaging shoes and that the last mentioned means is connected to the working assembly in a position to permit the floating frame moving vertically in the tracks relative the main frame when the shoes raise over an obstruction.

8. The apparatus of claim 6 further characterized in that there is provided means for locking said linkage in a given pivoted position, a bogey wheel assembly removably mountable on the working assembly to move in a direction at right angles to the working direction and support the working assembly, and that the wheel mounting means includes means for movably mounting one of the wheels on one portion of the main frame to selectively move in a working direction and in a transport direction.

9. The apparatus of claim 6 further characterized in that the wheel mounting means includes means for'mounting one of the aforementioned wheels for rotation in a working direction and alternately in a transport direction at right angles to the working direction, and that there is provided a bogey wheel, and means for removably mounting said bogey wheel on the working assembly to support it in an elevated direction and to move in a transport direction.

10. For being towed by a towing vehicle, a machine having a working width substantially greater than its overall length comprising a main frame, a first wheel mounted on one transverse side of the main frame for movement in the working direction, a second wheel, means for mounting said second wheel on the opposite transverse side of the main frame for movement in the working direction and alternately for movement in a. transport direction at approximately right angles to the working direction, a working assembly for performing a working operation adjacent the ground, means for movably mounting said working assembly on the main frame to extend longitudinally beyond the main frame for movement between an elevated transport position and a lowered working position, bogey wheel means removably mountable on the working assembly in longitudinal spaced relation to the second wheel to at least partially support the working assembly in an elevated position for movement in a transport direction, a tow bar, means for securing one end of the tow bar to the towing vehicle, means for attaching the opposite end of the tow bar to the main frame adjacent the first wheel for movement relative to the main frame both horizontal and vertical between a position extending in a forwardly extending direction to tow the vehicle in a working direction and a second position for towing the vehicle in a transport direction, means for releasably holding the tow bar in a generally forward direction against both vertical and horizontal movement, means for limiting the vertical movement of the tow bar in the transport position, means for urging the tow bar in a vertical direction in the last mentioned position to lift the first wheel off the ground when the tow bar is connected to the towing vehicle and the bogey wheel is mounted on the working assembly, first means mounted on the main frame for selectively moving the working assembly between a working position and a transport posi tion and second means cooperating with said first means to raise the second wheel off the ground when the bogey wheel is attached to the working assembly and the tow bar is connected to the towing vehicle in a forwardly extending position.

11. The structure of claim further characterized in that the second wheel mounting means includes a first plate fixedly secured to the main frame, a second plate hingedly mounted on the first plate for movement about a vertical axis between a transport position and a working position, means for selectively securing the plates in either of said working and transport positions and means connected to the second plate for journalling said second wheel for rotation.

12. The apparatus of claim 10 further characterized in that the working assembly mounting means includes means mounting the working assembly for arcuate movement relative to the main frame and that there is provided resilient means connected to the working assembly for constantly urging the working assembly to arcuately move to an elevated position.

13. A vehicle having a working width greater than its overall length comprising a main frame, a first wheel mounted on one transverse side of the main frame, a second wheel on the opposite side of the main frame, means for alternately securing the second wheel on the main frame to rotate about the same axis as the first wheel and about an axis 90 relative to the first mentioned axis, a tow bar, means connecting said tow bar to the main frame on the same general transverse side of the main frame as the first wheel for movement between a position extending generally horizontally forwardly of the main frame and a transverse inclined position extending generally in a direction parallel to the axis of rotation of the first wheel, the last mentioned means including means for releasably retaining said tow bar in the forwardly extending position, means permitting vertical movement of the tow bar in the transverse position and means for exerting a force on the tow bar tending to move the forward end of the tow bar in a downward direction relative to the main frame, a floating frame, means mounting said floating frame on the main frame for limited vertical movement relative thereto, a flail chopper assembly, means for securing said flail chopper assembly to the floating frame for arcuate movement relative thereto between a raised position relative to the ground and adjacent the ground and vertical movement with the floating frame, said flail chopper assembly extending a substantial distance forwardly of the main frame, means pivotally mounted on the main frame and pivotally connected to a longitudinal midportion of the flail chopper assembly for arcuately moving it between the elevated position and the lower position, the last mentioned means including a piston cylinder combination, elongated linkage means pivotally connected at one end to the piston cylinder combination and pivotally connected at the other end to the main frame and stop means for limiting the pivotal movement of the linkage means in a flail assembly lowering direction.

14. The apparatus of claim 13 further characterized in that there is provided a bogey wheel assembly including a transport wheel, said flail chopper assembly and bogey wheel assembly having cooperating means for removably mounting said transport wheel forwardly of the axis of rotation of the first wheel in the working direction to rotate about an axis at approximately right angles to the working direction.

15. The apparatus of claim 13 further characterized in that the flail chopper assembly includes a recutter assembly, a blower for exhausting the material cut by the recutter assembly, a flail chopper, an anger for receiving the material cut by the flail chopper and delivering it to the recutter assembly, said blower, auger, recutter assembly and flail chopper assembly each having a drive shaft, each of the aforementioned drive shafts being mounted parallel to one another, unending continuous means for drivingly connecting said drive shafts, one of said drive shafts being mounted to be coextensive with the axis of arcuate movement of the flail chopper assembly, and means for driving said one of the drive shafts.

16. The apparatus of claim 13 further characterized in that the flail chopper assembly includes end walls, ground engaging shoes mounted on said end walls, flail chopper mechanism journalled for rotation on said end walls, a plurality of auxiliary ground engaging shoes, means for mounting said auxiliary shoes in transverse spaced relation intermediate said end walls at a slightly higher elevation than the first mentioned shoes, at least one of said auxiliary shoes being of a wide width to ride on the ridge of an irrigation ditch or the like.

17. In a vehicle having working width of a greater dimension than its overall length, a main frame, wheels supporting said main frame for movement, a tow bar, means mounting said tow bar for movement between a position extending generally in a forward direction for towing the main frame in a working direction, and a transport position extending generally at right angles to the working direction and movement in a vertical direction, said tow bar mounting means including a universal joint connecting one end of the tow bar to a front side portion of the frame and means for holding the tow bar against vertical movement relative to the frame when the tow bar is in a forwardly extending position and permitting limited vertical movement relative to the frame in a transport position, means for selectively retaining the tow bar in either of said positions, said tow bar retaining means including means for selectively moving the opposite end of the tow bar in a downwardly vertical direction relative to the portion of the frame to which the tow bar is connected when the tow bar is in the transport position and the opposite end of the tow bar is elevated relative to the ground, means for mounting a first wheel on the side opposite the tow bar in position for rolling in the forward working direction, and alternately in a position for rolling movement in a transport direction, means for mounting a second Wheel on the opposite side of the main frame from the first wheel and a bogie wheel assembly having a transport wheel, said vehicle and bogie wheel assembly having cooperating means for removably mounting the transport wheel to roll in a transport direction and in conjunction with the second wheel support a 13 part of the weight of the vehicle as it is being moved in a transport direction.

18. In a vehicle having a working width of a greater dimension than its overall length, a main frame, wheels supporting said main frame for movement, a tow bar, means mounting said tow bar on the frame for movement between a position extending generally in a forward direction for towing the main frame in a working direction and a transport position extending generally at right angles to the working direction, and for movement in a vertical direction while in the transport position, said tow bar mounting means including a universal joint connecting one end of a tow bar to a front side portion of a frame and means for holding the tow bar against vertical movement relative the frame when the "tow bar is in a forwardly extending direction and permitting limited vertical movement relative to the frame in a transport position, means for selectively retaining the tow bar in either of said positions, said tow bar retaining means including means for selectively moving the opposite end of the tow bar in a downward vertical direction relative to the portion of the frame to which the tow bar is connected when the tow bars opposite end is elevated relative to the ground, means for mounting the first wheel on the side opposite the tow bar in position for rotation in a forward working direction and alternately in position for rolling movement in a transport direction, means for mounting the second wheel on the opposite side of the frame from the first wheel, a working assembly, means pivotally mounting said working assembly on the main frame spaced in the working direction therefrom for movement between a raised position relative the main frame and a lowered working position, means connected to the main frame for operating the working assembly mounting means between a raised and lowered position, a bogie wheel assembly having a transport wheel, said bogie wheel assembly and working assembly having cooperating means for removably mounting the transport wheel to roll in a transport direction and in conjunction with the second wheel support a part of the weight of the vehicle as it is being moved in a transport direction.

References Cited in the file of this patent UNITED STATES PATENTS 2,672,721 Adams Mar. 23, 1954 2,833,105 Naery May 6, 1958 2,836,952 Hume June 3, 1958 2,947,129 Kowalik Aug. 2, 1960 

1. FOR BEING PULLED BY A POWER VEHICLE, AN AGRICULTURAL IMPLEMENT HAVING A WORKING WIDTH OF A SUBSTANTIALLY GREATER DIMENSION THAN ITS OVERALL LENGTH COMPRISING A MAIN FRAME, A FIRST AND A SECOND WHEEL, MEANS FOR MOUNTING SAID FIRST WHEEL ON ONE TRANSVERSE SIDE OF SAID MAIN FRAME TO ROLL IN A WORKING DIRECTION, MEANS FOR SELECTIVELY RETAINING THE SECOND WHEEL ON THE OPPOSITE SIDE OF THE MAIN FRAME FOR ROLLING MOVEMENT IN A TRANSVERSE DIRECTION AND A LONGITUDINAL WORKING DIRECTION, A TOW BAR, MEANS CONNECTING ONE END OF THE TOW BAR TO THE FRAME ADJACENT THE SIDE ON WHICH THE FIRST WHEEL IS MOUNTED TO ALTERNATELY EXTEND GENERALLY IN A WORKING DIRECTION AND AT RIGHT ANGLES TO THE WORKING DIRECTION, THE LAST MENTIONED MEANS INCLUDING MEANS FOR FORCING THE TOW BAR TO MOVE ITS OPPOSITE END IN A DOWNWARD DIRECTION RELATIVE TO THE FRAME TO EXERT A TIPPING FORCE ON THE FRAME WHEN THE TOW BAR IS CONNECTED TO A TOWING VEHICLE AND RETAIN THE TOW BAR OPPOSITE END IN A RELATIVE DOWNWARD POSITION, A BOGEY WHEEL, AND MEANS FOR REMOVABLY CONNECTING THE BOGEY WHEEL TO THE MAIN FRAME IN LONGITUDINALLY SPACED RELATION TO THE SECOND WHEEL TO ROLL IN A TRANSPORT DIRECTION. 